Pump or compressor



Jan. 25,1927. v 1,615,257 G. J. BOONZAIER ET Ai.

PUMP OR coMPR Ess 0R Filed June 4. 1924 5 Sheets-Sheet 1 In we 7; 2 071are arz'a 70? 20071 2 1 flffarn 4/ Jan. 25, 1927. 1

- G. J. BOONZAlER ET AL PUMP OR COMPRESSOR Filed June 4, 1924 5Sheets-Sheet 2 are orz a ZZZ 200223.225

Patented Jan. 25, 1927.

unit an STATE as I? ATENT OFFICE.

GREGORIO JOHN BOONZAIER AND SIDNEY HARTLEY,- OF LONDON, ENGLAND,, AS-

SIGNORS TO BRITISH 8c COLONIAL INVENTIONS LIMITED, OF E. C. 4, ENGLAND.

PUMP OR COMPRESSOR:

Application filed. June 4, 1324, Serial No. 717,745,- and-in GreatBritainDecember. 8, 1923.

The present invention relates to improvements inpumpsior compressors ofthereciprocating type in which ports or openings ar angediin the pistonare adapted to eo-operate with other ports in the. wall of the cylinsdcr. or casing, thus. doing away wit-h the use of poppet, slide or othervalves or controlling means.

In addition to its reciprocatingmovement, the piston is, according to,the invention, given a continuotu rotary motion in one, direction aboutits longitudinal axis, thus avoiding the drawbacks andlossoit efiiciencyusual with that type of pump or compressort in which the Valve pistonhas a, rotary oscillating movement, such. asv is described in thespecification ot' Boonzaiers Patent No. 1,488,691 granted December 12,1922.

Inconstructing apump oft-he double-acting type, the piston consists of acylinder open at both ends, and havingacentral cross diaphragm or wallto which the piston rod is attached, thus forming two chambershaving'their openings arranged in opposite directions. The wall of eachchamber is provided with a port or ports which may be of rectangularshape or of a spiral or other shape, adapted to come into alignment withthe inletport or, ports or outlet port or ports of the pump cylinder 0rcasing as the piston is reciprocated and rotated therein.

The ports in the vupper and lower halves of thepiston are so arrangedasto produce the desired opening of the suction port in the cylinder andthe closingof the delivery port in the necessary sequence.

Generally the cylinder, or, casing will be provided with a suction porton one side and a delivery port on the diametrically, opposite side,while eachpiston chamber, will have one port, althoughthe piston may,have three or other odd number of ports, at equaldistances apart in somecases; for example, if the piston has three ports they will bespacedapart at 120 each, whereas if it is provided with five ports they,will be atv 72.

The number; of reciprocations of; the piston relatively to one completerotation thereot, will be arranged in accordance with the number ofports in the piston, and the following formula may generally beadopted,i. e. the number of complete reciprocations ot' the piston to onecomplete rotationot' piston will be equal to the sum of half the numberof ports in the. casing multiplied by the number of ports, in thepiston, (or in the one end of the pistononly in the case of a doubleact.- ing pumpi. v

lhe reciprocat ng motion of the piston may. beobtained by means of acrankshaft, or, the pistonmay. be driven direct from. the steam chest:of the motor engine, or other means, suchas avca m, working on thepiston or connecting rod, or. an extensionthereof may. be employed forthat purpose, the arrangement being such, however, that continuous,rotation of the piston is provided for.

This rotation may be effected by means of a bevel :wheel, mounted on thepiston rod and driveniby bevelgearing on the driving shaft orcrankshaft, the connection of the bevel wheel to'the piston rod beingsuch that its reciprocating motion will notbe interfered with.

VVhilewe have referred to the rotary motion of the piston as beingeifectedby bevel gearing, it. may also be effected by means of combinedbevel and'spur gearing, by combined crown wheel and spur gearing, bycombined bevel gearing and chain, by chain gearing, by worm and wormwheel, or by a cam. :levice or, other suitable means, and one or otherofthe above means may be also employed to obtain the reciprocatingmotion.

The accompanying drawings illustrate, examples of the construction andof the tunetioning of apparatus embodying the inven tion.

Fig. 1 shows a double-acting vertical surface pump, driven by acrankshaft, inside elevation, and

Fig. 2is a vertical section of the same on the line 22 of Fig. 1.

Fig. 3 is a cross section on the line 3-3 of. Fig. 2.

Fig. l is a cross section on the line l& ofFig. 2.

Fig. 5 is a similar section on the line 4-4: of Fig. 2 when the pistonis at the topend of its stroke.

Fig. 6 is a cross section on the line 66 of. Fig. 2, but assuming thepiston tobe in the middle of astroke.

Fig. 7 shows diagrammatically, in cross sections and their development,the different relative positions ofthe piston ports to the suction anddelivery ports during a double stroke of the pump shown in Figs. 16 inwhich the ratio of a double stroke to the rotary motion of the piston isone to one, while Fig. 8 is a similar diagram showing cross sectionsonly of the relative positions of the piston and cylinder ports duringhalf a revolution of the piston in a pump in which the piston is adaptedto perform three complete double strokes while efi'ecting onerevolution.

Fig. 9 shows the head of a pump having its driving gear connecteddirectly to the piston rod of a steam or other engine.

In the double-acting surface pump illus trated in Figs. 1 to 6, thecylinder is constituted by casing 1, the bore of which has a lengthsubstantially three time the length of the piston stroke. Centrally ofits length the cylinder is provided with diametrically opposite ports: asuction port A and delivery port B, both of substantially rectangularshape and having an axial length rather exceeding the piston stroke.

In the part of the cylinder extending above the ports A and B, a closedcylindrical inward projection 3 of a top cover 4 forms an annular recess2 in the cylinder, the inner fiat face of said projection, which is inalignment with the top edges of the ports A and B, constituting theupper limit of the working chamber C which is thus situateddiametrically across the cylinder between the said ports. The bottom ofthis working chamber C is formed by a cushion of the fluid which, in theworking of the pump, fills the lower part of the cylinder below theports A. and B. Incidentally, in the case of a pump this pocket alsofunctions as a sump in which sand or other solid matter may settle.

The piston 5 is provided at both sides with hollow cylindricalextensions or skirts 5 and 5 fitting the bore of cylinder 1, and of alength slightly exceeding the length of stroke.

The skirt 5 is provided with an aperture or piston port a and the skirt5 with a similar aperture or piston port a, the two piston ports beingarranged at diametrically opposite sides of the skirts 5 and 5 Thepiston 5 is secured to the piston rod 6, which is adapted to rotate andslide axially within a sleeve 3, formed centrally in the projection 3 ofthe top cover 4.

The driving gear is mounted on a support or pedestal 7 supported on thetop of the cylinder 1. The pedestal 7 carries, preferably formedintegrally therewith, a pair of vertical guide rails 8 for a crosshead9, from the lower end of which the end 6 of the piston rod 6 isrotatably suspended. Transverse beams 10 rigidly secured to the guiderails 8 so as to provide lateral guidance for the cross-head 9, form thebearings for a cranked driving shaft 11, which, when actuated in anyconvenient manner, imparts reciprocatory motion to the crosshead 9 bymeans of its crank 11 and connecting rod 12, which latter is connectedto the crank pin 11 and the wrist 9 of the cross head 9.

In order to reduce the height of the driving gear and thereby of thepump, the cross-- head 9 is preferably formed as a yoke embracing thecrank 11 and the connecting rod 12, as shown.

A continuous rotary motion is transmitted to the piston 5 from thedriving shaft- 11 by means of bevel gears 13, 1 1. The gear 13 ismounted on the shaft 11, while the gear 14 is mounted on a squaredportion 6 of the piston rod 6, this arrangement allowing the latter toslide axially in the wheel 14, which is rotatably journalled but securedagainst axial displacement in a bearing 15 arranged in the top plate 7of the pedestal 7 The reciprocatory as well as the continuous rotarymotions of the piston 5 are thus derived from the same source viz. fromthe crank shaft 11.

In the example illustrated in Figs. 1 to 7, these motions aretransmitted at the ratio of 1 to 1, that is to say, the piston is causedto execute one complete revolution to every revolution of the crank orto every double stroke of the piston.

The ports of the piston skirts 5 and 5" are so positioned angularly inrelation to the suction port A and the diametrically opposite deliveryport B that complete closure of all ports is co-incident with the end ofeach single stroke of the piston, while the area open, both on thesuction side A and on the delivery side B, reaches is maximum at themiddle of each individual (up or down) stroke.

The opening and closing of the ports at various stages in the course ofa complete double Stroke as performed by the pump l'iereinbeforedescribed in connection with Figs. 1 to 6, is illustrated in thediagrams comprising Fig. 7, in which the axial as well as the radialpositions of the piston and its ports are shown not only in developmentsof the contacting surface of the cylinder 1 with the piston skirts 5 and5 but also in cross sections. These cross sections, being intended toshow the angular relative positions only of the piston and cylinderports, are taken, as regards the cylinder, centrally through the suctionand delivery ports, and, as regards the piston, through the upper andlower piston skirts on planes above and below the piston respectively.without regard to the axial relative positions of the piston and thecylinder.

In these diagrams, that is to say, in the developments of the cylinderand the piston walls, the uncovered portions of the cylinder wall areshaded by vertical lines. while those portions of the suction anddelivery ports A and B which, at the various stages illustrated, are incommunicationwith the pistonports, are shownby vertically andhorizontally crossed hatching representing suction and diagonallycrossed hatching representing delivery.

In the position I), the piston is represented at the top of its stroke,while D, D and D"'show the position of a down stroke; D thusrepresenting-the piston :at the middle of its stroke. After performingthe last quarter of'its down stroke, the piston arrives at the. bottomend of its stroke represented in the diagram at U, from which positionthe piston in its up stroke successively passes through the positionsUIP and-U (eachof nhich again illustrates the positions at thecompletion of successive quarterstrokes) back-to the position shown atD.

By following the piston on its down stroke (positions D, D D it willbeseen that the piston port a, which is in front as regards the directionof movement of the piston 5,.co-operateswith the delivery port B, whilethe piston port a, in the rear as regards the direction ofmovementof'the-piston 5, co-operates with the suction port A, and thaton the up stroke (positions U, U U the function of the piston ports aanda in relation to the ports A andB is reversed.

By comparing the positions D and U, which represent the piston at thebeginning of each single down or upstroke respectiveiy it will beclearly seen that: in the 1 course of each stroke (whether up or down)the piston has simultaneously performed one half'of a revolution.

As wiltfiirtlier be seen from these diagrams, all'ports are closed atthe end of'each stroke, that is during the reversing ofthereciproc-atory motionsofjthe piston, are gradually-.opened in' the firsthalf of the stroke untilat the middle of the stroke the piston portsregister to=their full Width with the the reciprocating (double stroke)and therotary motions of the piston be, for example,

' three to one, the bevel' wheel Ll. or other suitable gear wheel may bedriven by an intermediate speed reducing gear, so that while the gear14' and, consequently, the pistoneffect one revolution, the shaft 11and, conse ucntl v, its-crank 1-1! per-formthree.revolutions, thuscausingthe piston to execute three complete double strokes, or sixsingle strokes. in this case, one double stroke being performed by thepiston during one third of a revolution thereof, each of the pistonskirts and 5" will be provided with three ports, which are successivelybrought into co-operation with the diametrically opposite suction tonand cylinder ports (as regards their re-lative angular positions'onlyhowever) which areshown by cross-sectionsthroughthe cylinderl andthrough the. piston sleeves-5 and 5 110-consideration being-given inthediagrams to the axial relative positions. of such ports;

The-piston skirts 5 and 5 are each provided with-three ports a, b, 0,anda, b, 0 respectively, arrangediat 120 in each skirt and at 180 asregards the ports of. the two 8.0

skirts, thus constituting three pairs ofi'ports a, a, Z), W andc, 0whichwill1be brought successively into operation in successive strokesof 1 the piston.

Fig. 8- shows the relative positions of thepiston and cylinderports-from quarter-to quarter stroke through threevsingle strokes and asimultaneous half revolutionof the piston.

Aswill be seen, starting from -thehtop onthe down stroke, the pistonports: a and'a' cooperates with the suction and: delivery ports A and Brespectively, while on the following upstroke the port 6 opens to thedelivery port Band the port I) tothe suction port-A, the portsc and 0being brought at the end of the up stroke into a. position whereby theyare rendered operative on the succeeding down stroke in connection withthe. ports A and B respectively. As-will: be seen in the last of theseries of positions shown, the ports at and a are now again ready forcooperation, on the following up stroke, with the delivery side B andthe sue-- tion side A respectively. Similarly the ports I), b and 0, 0will be brought: into action in" the succeeding down and up strokesrespectively, after which the performance'issimilarly repeatedin everysucceeding six strokes of the piston. Eachsetr of piston ports will thusbe operative on every third stroke of the piston alternately on a downstroke and on an up stroke and also alternately in'co-operation with thesuction port and the delivery port.

As has been shown in the examples hereiubefore described, the number ofports in each piston skirt, when using one suction and one delivery portin the cylinder, is equalto the ratio ofthe number of reciprocations ofthe pistonto the revolutions thereof, withthe reservation however, thatsaidnumber ofpistonports and ratioinust always be an odd number Thereason for this reservation is to be found in the followingconsiderations.

Obviously, the two diametrically opposite cylinder ports (suction anddelivery) must never be opened simultaneously to the ports on one sideor skirt of the piston, i. e. no two ports in the same piston skirt mustbe diametrically opposite each other. At the same time the fact that thestrokes of the piston are always of uniform length and duration,necessitates an equidistant distribution of the piston ports over thecircumference thereof. A fulfilment of these two conditions is onlypossible by the arrangement of an odd number of ports in each pistonskirt.

Fig. 9 shows an arrangement in which the pump is directly coupled to andoperated by the piston rod 17 of a steam or other engine which isconnected in any suitable manner, such as for instance, by bolting aorosshead 17 of the piston rod 17 to flanges 9 provided on the crosshead9 of the pump gear.

The piston rod 6 of the pump thus receives its reciprocating movementsdirectly, through the intermediary of the crosshead 9, from the saidengine, while it is now the crosshead 9 which, through the connectingrod 12 and the crank 11, imparts rotary motion to the shaft 11 fromwhich such rotary motion is transmitted at the desired ratio, forinstance, by means of the bevel gear 13, 1.4 or other suitable orreducing gear, to the piston rod 6 of the pump in the mannerhereinbefore described.

\Vhile the foregoing description has reference to a double-acting pump,the simple omission of one of the piston skirts renders the pump asingle-acting one, in which obviously the length of the cylinder may bereduced so as slightly to exceed only the double length of the stroke.In all other respects, including the arrangement and numher of pistonports, the single acting pump may be arranged in the same manner as thedouble acting pump hereinbefore described.

In some cases, particularly where the apparatus is to be used for thecompression of air or the like, we ma instead of providing the pistonwith open ended skirts, form the said piston as a solid member or as ahollow member with closed ends. In such an arrangement, the piston portswill then be constituted by grooves or channels formed in the outersurface of the piston and extending longitudinally of the same; forexample, in the case of a double-acting piston making one completedouble stroke per revolution, there will be two diametrically oppositegrooves, one extending substantially from the top to the middle of thepiston in an axial direction, and the second diametrically oppositegroove extending substantially from the middle to the bottom thereof.

By reversing the direction of rotation of the crank shaft 11 the pumpwill operate in an analogous manner in the opposite direction.

What we claim is l. A pump or compressor, comprising a cylinder providedwith suction and discharge ports; a reciprocatory cross-head; operatingmeans therefor; a piston rod rotatably suspended from said cross-head tomove up and down therewith; a piston attached to said rod forcontrolling the cylinder ports during its movements; a gear wheelmounted on the piston red but held against reciprocatory movementtherewith; and means for rotating said gear wheel and thereby the pistonrod and piston during their reciprocation with the cross-head.

2. A pump or compressor, comprising a cylinder provided with suction anddischarge ports; a reciprocatory cross-head; operating means therefor; aframe wherein the cross-head is slidably mounted; a piston rod rotatablysuspended from said crosshead to move up and down therewith; a pistonattached to said rod for controlling the cylinder ports during itsmovements; and gearing for rotating the piston rod and piston duringtheir reciprocation with the cross-head and including a gear rotatablymounted in said frame and with which said rod is slidahly engaged.

3. A pump or compressor, according to claim 2, in which the piston rodis engaged with the frame-mounted gear in a manner to rotate with thatgear and to slide axially through the same during such rotation.

4. A pump or compressor, comprising a cylinder provided with suction anddischarge ports; a crank shaft rotatably mount ed above said cylinder; across-head connect:- ed to said shaft to be reciprocated thereby; aframe wherein the cross-head is slidably mounted; a piston rod rotatablysuspended from said cross-head and having a portion of polygonalsection; a piston attached to said rod for controlling the cylinderports during its movements; a gear rotatably fixed to said frame andhaving a polygonal opening through which the polygonal portion of thepiston rod slidably extends; and means for rotating said gear, and withit said piston rod and piston, during the rotation of the crank shaft.

In testimony whereof we aflix our signatures.

GREGORIO JOHN BOONZAIER. SIDNEY HARTLEY.

